Mining machine



Sept. 21, 1943. F. CARTLIDGE MINING MACHINE Filed Aug. 27, 1941 8 Sheets-Sheet 1 Sept. 21, 1943. CARTLIDGE MINING MACHINE Filed Aug. 27, 1941 8 Sheets-Sheet 2 1 0M intZ/a e 8m Sept. 21, 1943. F. CARTLIDGE MINING MACHINE Filed Aug. 27, 1941 8 Sheets-Sheet 3 mow \w m 2* 8 Sheets-Sheet 4 F. CARTLIDGE MINING MACHINE Filed Aug. 27,1941

Sept. 21, 1943.

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www www Sept. 21, 1943. F. CARTLIDGE MINING MACHINE Filed Aug. 27, 1941 8 Sheets-Sheet 8 Patented Sept. 21, 1943 UNITED STATES PATENT OFFICE MINING MACHINE Frank Cartlidge, Chicago, 111., assignor to Goodman Manufacturing Company, Chicago,-1li., a corporation of Illinois Application August 27, 1941, Serial No. 408,531 12 Claims. (01. 202-9) This invention relates to improvements in mining machines especially adapted for use in mining coal, and more particularly to combined mining and loading machines wherein the coal can be dislodged from the working face and gathered and loaded out by the same mechanism.

Among the objects of my invention is to provide an improved and eflicient form of picking mechanism for breaking down the coal face at various levels above the floor, with a novel form of undercutting and gathering mechanism cooperating with said picking mechanism in an especially efficient manner. A further object is to provide an improved form of extension frame for projecting the picking and gathering devices forwardly and rearwardly of the main frame under certain conditions. Other objects will appear from time to time as the following description proceeds.

The invention may best be understood by refer ence to the accompanying drawings, in which:

Figure 1 is a view showing in side elevation a machine constructed in accordance with my invention, but with a rear portion of the discharge conveyer omitted, and illustrating the manner of use of the machine in a mine, as it is attacking the working face;

Figure 2 is a side view of the machine showing the parts in position for transporting from one working place to another;

Figure 3 is an enlarged plan-view of the machine of Figures 1 and 2, with a part of the picking mechanism broken away at one side to show portions of the gathering mechanism;

Figure 4 is a side view of the machine, drawn to the same scale as Figure 3, showing the extensible frame in retracted position relative to the main frame;

Figure 5 is a view somewhat similar to Figure 4, but with certain parts shown in longitudinal section, and with the extensible frame in forwardly extended position;

Figure 6 is a transverse section taken generally on line 6-6 of Figure 3;

Figure 7 is a detail longitudinal section of one of the operating cylinders forming part of the picking mechanism, and showing the air piston in forwardly extended position;

Figure 8 is a detail section drawn to a larger scale and taken on line 8-8 of Figure 7 Figure 9 is a fragmentary detail, taken on the same section line as Figure '7, but drawn to a larger scale and showing the air piston in rearwardly retracted position;

Figure 10 is a fragmentary detail plan view at figures, showing the swinging discharge conveyer at the rear end of the machine;

Figure 14 is an enlarged transverse section of the swinging discharge conveyershown in Figure 13;

Figure 15 is an enlarged fragmentary plan view in part section, showing details of the drive connections to the motor, and the control mechanism therefor;

Figure 16 is a detailtransverse section of one of the gathering arms in kerf-cutting position.

Referring now to details of the machine of my invention illustrated in the drawings, a base frame [0 is formed integral with a pair of longitudinal endless-tread supporting side frames H, and has an extensible frame l2 mounted thereon between said tread supporting frames. The extensible frame has mounted thereon a pair of picking devices l3, l3, a pair of gathering devices l4, l4, and a conveyer I5 leading upwardly from said gathering devices and overhanging the rear end of the machine. The endless-tread supporting frames II are provided as usual with a front end roller IS, a rear drive sprocket l8, and a plurality of intermediate guide rollers l6a, |8a for endless treads l1, l1 of well known construction.

It will be seen in Figures 5 and 6 that the base frame It extends transversely between the tread supporting frames II, and has a pair of upstanding trunnions l9, l8 disposed at opposite sides thereof which carry inwardly projecting trunnion studs 20, 20 pivotally engaged in elongated side bars 2|, 2|. Said side bars are telescopically mounted in slots 22, 22, undercut as shownin Figure 5 and extending horizontally along opposite sides of side frame members 23, 23 of the extension frame l2. with this arrangement the extension frame is telescopically slidable relative to the side bars 2|, 2|, and said extension frame. together with the side bars 2|, is also tiltable endwise about the trunnion studs 20, 2|].

The side bars 2| have transversely disposed pins 24 at their rear ends. each engaged by a bifurcated arm 25 of a bell crank lever 26 (see consisting of bosses 21, 21 formed integral with the tread supporting frames II. The bell crank levers 26, 26 are rocked by power to tilt the entire extension frame l2 on the trunnion studs 20, 2B. In the form shown, said bell crank levers are rocked by a pair of hydraulic cylinder devices 30, 30 pivotally mounted on the base l0, and having their pistons 3|, 3| pivotally connected to the upright arms of said bell crank levers. Hydraulic pressure to the cylinders 30, 30 may be supplied as usual from a pump, under manual control of suitable valves (not shown).

The tilting adjustment of the extension frame l2 relative to the base l may be noted in Figure 2, wherein the front end of said extension frame is tilted upwardly to elevate the gathering devices from the ground, and thus facilitate transportation of the machine from place to place.

The extension frame I 2 is moved forwardly and rearwardly relative to the base l0 and its endless treads by means of a horizontally disposed hydraulic device 33 pivotally connected to said base and having its piston 34 connected to a cross member 35 at the front end of the extension frame l2 (see Figures and Hydraulic pressure may be supplied as usual to the front and rear ends of the cylinder 33 through pipes 36 and 31, under control of suitable valves, not shown.

The two pick devices |3, |3 are pivotally mounted at their rear ends on upright pedestals 40, 40 formed integral with the side frame members 23, '23 at opposite sides of the extension frame l2, so that said pick devices may swing in a vertical plane. In the preferred form shown, said pick devices are designed for simultaneous actuation of a plurality of picks 4|, 4|, herein four in number, mounted on a cross head 42 connecting ram members 43, 43 reciprocatingly operated by said pick devices (see Figure 3) The pick devices l3 are similar in construc-- tion and are shown in detail in Figures 6, 7, 8 and 9. Each includes an air cylinder 45 having a piston 46 therein, operatively connected to the ram member J 43 by a hydraulically controlled telescopic extension cylinder 41, as will presently be described in detail. Said extension cylinder is slidably mounted in abarrel portion 44 rigidly connected to the front end of the air cylinder 45.

Each air cylinder 45 is mounted forwardly of a housing 48 which formsthe pivotal support for the pick. In the form'shown. said housing has an inner side wall 49 with a boss 58 jouralled in an upright wing 40a of the pedestal 40, and an outer side wall 5| which is journalled on an outwardly projecting boss 52 of a second upright wing 40b of said pedestal. The boss 52 of said pedestal also provides bearing for a crank shaft 53 having a chain sprocket 54 at its outer end, which forms part of a mechanical drive for actuating the pick, as will presently appear.

A coil compression spring 55 is mounted on the front end of the barrel 44 between a flanged portion 44a on said barrel and a collar 41a. fixed on the projecting front end of the telescopic extension cylinder 41.

The piston 45 is actuated mechanically for detentis adapted to be engaged by a roller 54 carried on a lever arm 51 pivotally mounted in a hollow block 58 which has reciprocable movement alonglongitudinal guide members 59. 53. A second roller 55a is also carried by the lever arm 51,.oifset laterally fromroller 55. The lever arm 51 is normally maintained in detent-engaging position by a spring 50. The crank shaft 53 at the outenside of the housing 48 has a crank arm 5| thereon, carrying a roller 82 which moves between a pair of opposed vertical guides 53, 63 carried on the adjacent side of theblock 58 (see Figure 7). With this arrangement, rotation of the crank shaft 53,produces reciprocating movement of the block 58. The driving means for the crank shaft will presently be described.

With the roller 55 engaged with detent 55c and the piston 45 in its forwardmost position as shown in Figure '7, a half revolution of the crank shaft will retract the piston by power so as to compress the air in the rear end of cylinder 45. Simultaneously, the coil spring 55 surrounding the front end of the telescopic extension device 41, will be compressed. As the piston 48 and the block 58 reachesthe rear limit of their stroke, as shown in Figure. 9, the roller 56a is engaged by a cam member 65 projecting from the rear wall 66 of housing 48, so as to lift the roller 58 from said detent member, thereby releasing the piston for a rapid forward stroke, under pressure of the airin cylinder 45 and the compression spring 55. Upon continued rotation of the crank shaft, the block 58 will again be moved to the initial position shown in Figure 9, so that the roller 58 will again engage the detent member 550, and repeat thecompressing movement and quick release of the piston 46 previously described. The spring 55 insures full return of the piston and ram to their forward position for the beginning of each compression stroke.

A check valve 51 is provided near the rear end of the air cylinder 45, communicating with the outer air, which valve operates automatically to replenish air which may be lost by leakage while the piston is under pressure. Suitable relief vents 58, 88 may also be provided at the low pressure end of the cylinder, as shown in Figure '7, of such size and arrangement to afford a desired amount of air cushioning action at the front end of the air cylinder as the piston approaches the forward limit of its stroke.

Details of the hydraulic extension cylinder 41 are shown in Figure '1. Said cylinder consists of an outer shell 10 and a concentric inner shell 1|, both rigidly connected at their rear ends to the front face of the piston 46, as by threading in a centrally disposed recess 12. The two shells are spaced from each other and sealed by annular rings 13.and 14 at opposite ends, and by an intermediate ring 15, so as to form two chambers 16 and 11.

The outer shell 10 is slidably mounted in spaced relation within the barrel 44 by liquid-tight packing sleeves or glands 18 and 19 at the rear and front ends of said barrel, and by an intermediate packing sleeve or gland 80, herein mounted within the flanged portion 44a of said barrel. The packing sleeves thus. described form partitions for two chambers 82 and 83 at front and rear of the barrel 44.

The inner shell 1| has a piston 43a therein, rigidly connected to the rear end of the ram 43. The front end of said ram extends through a liquid-tight packing sleeve or gland 84 at the front end of the inner shell.

Hydraulic pressure for extending or retracting the ram 43 is introduced through two flexible pipes 85 and 86, communicating respectively with the chambers 82 and 83 surrounding the outer shell 10. Pressure to the front end of piston 43a is supplied through port 81, formed in the outer shell adjacent the'front end of the chamber 82, so as to communicate with the chamber 11 between the inner and outer shells. From the latter chamber, a port 88 at the front end communicates with the interior of the inner shell H in front of the piston 43a.

Similarly, pressure is supplied from the outer chamber 83 to the rear end of piston 43a through port 89 formed in the outer shell 10 adjacent the front end of chamber 83, so as to communicate with the chamber 16, and from thence through a port 90 near the rear end of the inner shell 1 I, so as to apply pressure at the rear of the piston 43a.

The arrangement of the extension cylinder 41 and its associated chambers and ports just described, is such that the supply pipes 85 and 86 will be maintained in communication with the front and rear faces respectively of the piston 43a in all positions of reciprocating movement of the piston 46 in air cylinder 45, and in all permissible positions of extension of the ram 43 relative to said piston.

The front ends of the two extension cylinders 41 are rigidly connected by a cross-brace92, to insure simultaneous adjusting movement of said extension cylinders. The cross head 42, carrying the pick members I3, I3 and connecting the outer ends of the rams 43, is movable toward and away from said cross brace.

The operation of the picking mechanism is as follows: When the hydraulic extension means is adjusted to its rearwardmost retracted position, pistons 43a. are near the rear ends of the telescopic extension cylinders 41, as shown in Figures 3 and 7. The picking mechanism is preferably presented to a working face initially with the extension means in this retracted position, but with the coil springs 55 urging the extension cylinders 41 forwardly, and with the air pistons 46 at the front ends of their cylinders 45, as shown. Operation of the rotary retracting mechanism including crank arms 6| and the tripping mechanism associated with the guide blocks 58, as previously described, produces the desired retraction and quick release of the cross head 42 for its forward picking stroke. The springs 55 are compressed simultaneously with the air in cylinders 45 during the retracting stroke, and cooperate with the compressed air in said cylinders to produce the quick forward stroke.

The extension means is controlled by hydraulic pressure introduced through supply pipes 85 and 86 to opposite sides of pistons 43a. By maintaining balanced hydraulic pressures on opposite sides of said pistons, the extension means can be locked against longitudinal extending movement in any position of adjustment while said extension means reciprocates bodily with the pistons 46. When it is desired to advance the cross head toward the working face, the pressure on the rear piston 43a is increased temporarily to adjust the cross head to an extended position relative p I a to the piston 46. Similarly, the cross head can be retracted toward the piston 46 bytemporarily increasing the pressure on the front of pistons 43a. Since the hydraulic control of the'exten-- sion means is independent of the means controlling reciprocation of the piston 46, it will be noted that endwise adjustment of the hydraulic extension means can be effected at any time during I the operation of the picking mechanism.

It will be observed further, that while the picking mechanism usually will operate most efflciently with a full working stroke, yet my improved picking mechanism will perform very satisfactorily with only a partial stroke, in instances where the cross head may be advanced so close to the working that a full stroke is impossible.

In such cases the air in cylinders 45 will be as fully compressed at the beginning of the forward stroke as when operating with a full stroke, excepting after long-continued operation under partial length strokes, when air leakagefrom the cylinders may tend to reduce the operating pressure. However, as soon as full stroke operation is resumed, the springs 55 cooperate with pistons 46 to replenish the cylinders 45 with a full charge of air through check valve 61.

Means for swinging the picks I3, I3 in a vertical plane consists of a pair of hydraulic cylinders 95, 95, each pivotally connected at its lower end to the adjacent pedestal 40 and extending upwardly and forwardly with its piston rod 96 pivotally connected to a bracket 91 on one side of the air cylinder 45. Hydraulic pressure may be supplied to the cylinders 95 through the usual flexible. pipes, with valve control means thereof suitably mounted on the base frame.

The gathering devices I4 consist of a pair of cutter bars I00, I00 carried in forwardly projecting relation from the front end of the extension frame I2, in position to undercut the mine face, and to load out the material broken down by the pick devices I3, I3. Cutter chains IOI, IOI are suitably guided about said cutter bars. In the form shown, said cutter bars are widened at their front ends so that the inner reaches of the chains IOI, IOI approach each other fairly closely, but recede laterally from each other toward the rear ends of said arms. The outer reaches of the cutter chains are approximately parallel with each other, and are spaced apart substantially the full width of the cross head 42 of the pick devices I3, I3, as shown in Figure 3. The cutter bars are normally disposed in a horizontal plane close to the ground at their front ends, and are curved upwardly into an inclined plane at their rear ends. They are rigidly supported on annular bosses I02, I02 at opposite sides of a similarly inclined apron or plate I03 extending across the front end of the extension frame I2 and rigidly connected thereto as by brackets I04,

I04 at the front ends of the side frame members 23, 23 of said extension frame, as shown in Figures 10 and 11.

The cutter chains IOI each have a plurality of bit-carrying cutter blocks I06, I 06 of the type commonly employed in cutter chains of kerf-cutting machines. Said chains also carry a plurality of cutter blocks I01, I01, with integrally formed sweeper arms I08 projecting upwardly and inwardly therefrom in close proximity to the upper face of the cutter bar, as shown in Figure 16, so as to assist in sweeping the dislodged material rearwardly for loading on the conveyer I5.

The cutter chains IOI are each engaged with a sprocket IIO on shaft III, extending through and suitably journaled in the plate I03. The gearing for driving the sprockets H is shown in Figures 11 and 12. A gear H2 is keyed on each sprocket shaft III beneath the plate I03 and is meshed with a pinion H3 rotatable on bearings II3a on a stub shaft H4. The pinion H3 is integral with a bevel gear H5, driven by a bevel pinion H6 on a shaft H6a extending outwardly to the adjacent side of the machine where it has a. sprocket I I1 keyed thereon in position to be driven by a chain I I8, which will presently be described in greater detail. In the form shown, the gearing for each chain sprocket H0, just described, is enclosed and has suitable bearing in a housing H9 detachably secured to the bottom of the plate I03 for ready removal.

The conveyer I has a single endless chain I with transverse flights thereon mounted for movement along a forward inclined section I22 and a generally horizontal rear section I23. The forward section I22 is rigidly mounted on the extension frame I2, while the rear section I23 is pivotally movable on a transverse axis, to permit vertical adjustment at the rear or discharge end thereof.

The inclined front section I22 of the conveyer I5 includes two flared side walls I24, I24 having upper and lower bottom plates I25 and I26 connected therebetween, forming in effect a double decked trough for the upper and lower strands of the conveyer chain I 20. As shown in Figure 5, the lower bottom plate I26 is supported by the cross-member 35 of the extension frame I2. The side walls I24 of said front conveyer section extend forwardly between and are connected to the side wing portions I03a, I03a of the apron I63 (see Figure 12). The conveyer chain I20 passes over an idler shaft I21 suitably journaled in the front ends of said side plates, immediately adjacent the discharge edge I28 of the apron I03. The arrangement just described is such that the loose material, including lump coal and cuttings, dislodged either by the picks or the cutter bits, will be carried rearwardly by the cutter chains and be discharged upon the front end of the conveyer I5, between the side wings I03a, 103a.

The side walls I24 of the front conveyer section I22 are rigidly mounted at their rear ends on a cross frame member I29 carried on inward- 1y projecting brackets I30, I30 formed integral with the pedestals 40, 40, as shown in Figure 6. The cross frame member I29 includes a pair of spaced bearing supports I3I, I3I having a conveyer drive shaft I32 rotatably mounted therein. Said drive shaft has a sprocket I33 engaging the lower strand of the conveyer chain I20. An idler roller I35 is mounted on shaft I35a between the side walls I24 forwardly of the drive shaft I32, as shown in Figure 5, so as to increase the wrap of the cliain I20 about the sprocket I33. The bottom plate I26 of the conveyer is flared downwardly at I26a to accommodate the drive sprocket I33 and idler roller I35.

The drive shaft I32 extends laterally to one side of the machine, where it has a drive sprocket I35 forming part of a chain driving system which will presently be described in detail.

The rear section I23 of the conveyer is pivotally connected to the front section I22, so as to permit vertical swinging adjustment of said rear section. In the form shown, said connection consists of a pair of side plates I38 at opposite sides of the rear section, pivotally connected by pins I39 to side plates I40 on the front I641: respectively, keyed on sleeve I65.

section, as shown in Figures 6 and 13. The rear section is elevated and lowered by a hydraulic cylinder I4I, pivotally connected to the crossframe member I29 and having its piston rod I42 pivotally connected to a bracket I43 on the under side of the rear conveyer section I23, as shown in Figure 14. Hydraulic pressure may be supplied to the cylinder I H thrqugh the usual valve control means.

The rear conveyer section I23 also has an articulated joint indicated generally at I45, to permit lateral swing of the rear end portion of said section, by means of a hydraulic cylinder I46. The articulated joint shown herein is of the type disclosed in Patent No. 2,197,169, issued April 16, 1940, to C. E. Andershock, and details thereof need not be described herein as it forms no part of the present invention.

Referring now to the means for driving the several mechanisms previously described, including the picking devices I3, I3, the gathering devices I4, I4 and the conveyer I5, the machine shown herein has a single motor I50, with chain drive connections to said mechanisms operative in all positions of extension or retraction of the extension frame I2 relative to the base I0. Said motor is mounted on the base I0 between the tread supporting plates II, as shown in Figures 6 and 15, and has an armature pinion I5I selectively engageable with a cross shaft I49 through a bevel gear I53, disc clutch housing I54, and a cone clutch indicated at I55. The opposite ends of cross shaft I49 extend through the tread supporting plates II, .II and bosses 21, 21 connected therewith, and have sprockets I56, I56 thereon disposed outside of the endless treads I1, II, as shown in Figure 15. A drive chain I51 is trained over each of said sprockets, with its lower reach extending forwardly over the sprocket II1 on shaft H6, for driving the cutter chain I00 of the gathering device I4 at one side of the machine. From thence the chain passes rearwardly and upwardly over sprocket 54 on crank shaft 53 which drives the picking device I3 on the same side of the machine. The drive chain I51 then passes forwardly over an idler sprocket I58 mounted on bracket I59 at the front end of the extension frame I2, and thence returns rearwardly to the drive sprocket I56. With the arrangement of idler sprocket just described, the drive chain will be maintained at substantially uniform tension in all telescoping and tilting positions of the extension frame I2 relative to the base frame I0.

The conveyer drive shaft I32 is driven by a chain I60 connecting sprocket I36 on the outer end thereof with a sprocket I6I keyed on the crank shaft 53 at one side of the machine (see Figure 7).

The motor I50 also drives the endless treads I1 through the gearing shown in detail in Figure 15. The motor pinion I52 is constantly meshed with the gear I53 on clutch housing I54 previously mentioned, and with gear I63 on a companion clutch housing I64, so that the two clutch housings are rotated in opposite directions. Said clutch housings I54 and I64 are loosely mounted on a. sleeve I65, which in turn is loosely mounted on cross shaft I49. Said clutch housings have friction clutch discs of conventional form therein. for selectively driving clutch members I54a and Said clutch discs are engaged by pressure plates I54b and I64b respectively, which are operated by a 1 push rod I66 on a common shifter ring I61, so

that only one of said clutches can be engaged at the one time, and both clutches will be disengaged when the shifter ring I" is in the central. or neutral, position shown.

The sleeve I85, rotatable reversely through the clutch mechanism just described, extends alon the shaft I49 and through suitable intermediate bearings I, to a planetary gear device indicated generally at I69. Said planetary is of the friction controlled type commonly employed in mining machinery, and includes a sun gear member I10 keyed on the sleeve I65, and a driven gear I ll operable, as usual, at reduced speeds through planetary gears I12, under frictional control of a brake band H3;

The drive gear I II is meshed with a gear I15 on a differential drive member I16. Said drive member carries a plurality of bevel gears I'Il meshed as usual with bevel gears I18, I18 on the adjacent ends of drive shafts I19, I19. The tread drive sprockets l8, I8 are keyed on the outer ends of said drive shafts. Brake drums I80, I80 may also be carried on said drive shafts.

While I have herein shown and described one form in which my invention may be embodied, it will be understood that the construction thereof and the arrangement of the various parts may be altered without departing from the spirit and scope thereof. Furthermore, I do not wish to be construed as limiting my invention to the specific embodiment illustrated, excepting as it may be limited in the appended claims.

I claim as my invention:

1. In a, cutting and loading machine, a base having ground-supported propelling devices, a supporting frame telescopically and rockably mounted relative to said base, gathering devices including a pair of chain-carrying cutter bars projecting at the front end of said supporting frame and a picking device pivotally mounted for vertical swinging adjustment on said supporting frame above said gathering devices, whereby said gathering and picking devices may be bodily projected forwardly and rearwardly rectilinearly with said supporting frame in a plurality of planes relative to said base and its propelling devices.

2. In a cutting and loading machine, a base having ground-supported propelling devices, a

supporting frame telescopically and rockably mounted relative to said base, gathering devices including a pair of chain-carrying cutter bars projecting at the front end of said supporting frame and a picking device pivotally mounted for vertical swinging adjustment on said supporting frame above said gathering devices, whereby said gathering and picking devices may be bodily projected forwardly and rearwardly rectilinearly with said supporting frame in a plurality of planes relative to said base and its propelling devices, a motor on said base for driving said gathering and picking devices, and means affording operative connection between said motor and said gathering and picking devices in all extended and tilting positions of said supporting frame.

3. In a cutting and loading machine, abase, a pair of laterally-spaced, forwardly projecting gathering arms projectingforwardly from said base in a horizontal plane and having orbitally movable cutter chains thereon, an elevating conveyer on said base arranged to receive material from between said gathering arms and carry it along said base for discharge rearwardly thereof, and a reciprocating picking device pivotally mounted on said base for vertical swinging adjustment at various angles above said gathering arms, said picking device including a transverse picking bar and a pair of laterally spaced, reciprocably operable ram members connected to said bar and having means for extending or retracting said bar relative to the front ends of said gathering arms and conveyer.

4. In a cutting and loading machine, a base, a pair of laterally-spaced, forwardly projecting gathering arms projecting forwardly from said base in a horizontal plane and having orbitally movable cutter chains thereon, an elevating conveyer on said base arranged to receive material from between said gathering arms and carry it along said base for discharge rearwardly thereof, and a reciprocating picking device pivotally mounted on said base for vertical swinging adjustment at various angles above said gathering arms, said picking device including a transverse picking bar, and a pair of laterally spaced reciprocably operable ram members connected to said bar and having hydraulically actuated, telescopic means for extending or retracting said bar relative to the front ends of said gathering arms and conveyer.

5. In a mining machine, a base, a supporting frame having gathering devices at its forward end, and means for extensibly and tiltably mounting said supporting frame relative to said base including a pair of trunnions at opposite sides of said base, and a pair of elongated bars pivotally connected with each of said trunnions and ,having sliding engagement along opposite sides of said supporting frame.

6. In a mining machine, a base, a supporting frame having gathering devices at its forward end, and means for extensibly and tiltably mounting said supporting frame relative to said base including a pair of trunnions at opposite sides of said base, and a pair of elongated bars pivotally connected with each of said trunnions and having sliding engagement along opposite sides of said supporting frame, and means affording tilting adjustment of said supporting frame relative to said base including a control member mounted on said base and operatively connected to one of said elongated bars.

7. In a mining machine, a base, a supporting frame having gathering devices at its forward end, and means for extensibly and tiltably mounting said supporting frame relative to said base including a pair of trunnions at opposite sides of said base, and a pair of elongated bars pivotally connected with each of said trunnions and having sliding engagement along opposite sides of said supporting frame, and means affording tilting adjustment of said supporting frame including a rocking lever pivotally mounted on said base and engaging one of said elongated bars.

8. A reciprocating picking device for loading machines including a ram, a piston connected to said ram, an air cylinder for said piston, rotary retracting mechanism acting on said piston, to compress air in said cylinder, a compression spring for supplementing the compressive action of said piston and normally urging the latter to the forward end of its stroke, and tripping means for automatically releasing said piston at the end of its compression stroke in said cylinder.

9. A reciprocating picking device for loading machines including a ram, a piston connected to said ram, an air cylinder for said piston,

rotary retracting mechanism acting on said piston to compress air in said cylinder, a compression spring normally urging said piston to the forward end of its stroke and tripping means for automatically releasing said piston at the end of its compression stroke in said cylinder, said cylinder having a check valve at its compression end affording replenishment of outside air to said cylinder during the return stroke said piston.

10. A reciprocating picking device for loading machines including an air cylinder having a piston therein, means for intermittently actuating said piston to compress air in said cylinder and releasing said piston while under such com-.

said ram, an air cylinder for said piston, rotary retracting mechanism acting on said piston to I compress air in said cylinder. a compression spring for supplementing the compressive action of said piston and normally urging the latter to the forward end of its stroke, and tripping means for automatically releasing said piston at the end of its compression stroke in said cylinder, said cylinder having a check 'valve at its compression end affording replenishment of outside air to said cylinder during the return stroke of said piston.

12. A reciprocating picking device for loading machines including a pick member, a casing, a reciprocating actuating member for said pick member in said casing, and extension means interposed between said pick member and said actuating member and reciprocable with the latter, including a ram connected tosaid pick member, a cylinder connected to said actuating member and slidable therewith in said casing, and hydraulic pressure supply means connected to said casing and affording communication with opposite ends of said hydraulic cylinder in all of the reciprocating positions of the latter in said casing.

FRANK CARTLIDGE. 

